Transmission control



Nov. 28, 1939. Q w To 2,181,647

TRANSMISSION CONTROL Filed April 16, 19.34 8 Shegets-Sheet l E Q N3 Q mu I TQ \q 1|! l R xmv Mm. mx Q o R g Q I I Ma .Il \w I w R. I I'M. I M I II "in" I/ N l II IQ w 0. R I I o 6 5 I mm w e \m .1I Q Q Q m W R QM II w I MN MW v o 0 III III I I a o v Q n Q. I III I m3 I o Q SSW H Nov. 28, 1939. E. o. WHEATON TRANSMISSION CONTROL' I 8 Sheets-Sheet 2 Filed April 16, 1934 Q L {I R? w \w l \N w Q I fi 1 v i, Q Q w H 3 Q 1 m @w I 1 QM. R w Q v x Q s 0 mm N I 1 \8 m\\ Nov. 28, 1939. E. o. WHEATON TRANSMISSION CONTROL 8 Sheets-Sheet 4 Filed April 16, 1954 Nov. 28, 1939. I E. ov WHEATON "2,181,647

TRANSMISSION CONTROL Fild April 16, 1954 8 Sheets-Sheet 5 Nov. 28, 1939. E. o WHEATON TRANSMISSION CONTROL 8 SheetsSheet 6 Filed April 16, 1934 AMMM:

Nov. 28, 1939. E O WHEATON 2,181,647

TRANSMI S S ION CONTROL Filed April 16, 1934 8 Sheets-Sheet 7 Nov. 28, 1939. E. o WHEATON TRANSMISSION CONTROL 8 Sheefi-Sheet 8 Filed April 16, 1934 Patented Nov. 28, 1939 UNITED STATES 2,181,041 7 Transmission common Estcl o. Wheaten, Toledo, om, asaignor to Kelly-Wheaten Company, Toledo, Ohio, a corporation of Ohio Application Apr l 18. 1934. Serial No. 720.822

lclaim.

This invention has utility when incorporated in multispeed transmission with hydraulic cooperative control including connecting, disconnecting and speed change features, more especially as affected by the internal combustion motor in a motor vehicle and the rate of travel therefrom.

Referring to the drawings:

Fig. 1- is a section through the'housing disclosing an embodiment of the transmission hereunder;

Fig. 2 is a. section on an enlarged scale of portions of the transmission at the left in Fig. 1;

Fig. 3 is a section on the line IIIIII, Fig. 1, showing features of the hydraulic braking;

Fig. 4 is an enlarged view, with parts in section, of portions of the device on the line IV--IV, Fi 3;

Fig. 5 is a section on the line V-V, Fig. 1, showing a feature of the hydraulic connection at the planetary gearing;

Fig. 6 is a section on the line VI-VI, Fig. 1, showing features of hydraulic control at intermediate speed; a

' Fig. 7 is a view on the line VII-VII, Fig. 1;

Fig. 8 is a view of a modified type of overwinding clutch connection;

Fig. 9 is a view on the line IXIX, Fig. 8;

Fig. 10 is a section on the line X-X, Fig. 4, showing the reverse direction drive gearing;

Fig. 11 is a partial section on the line Jfl-XI, Fig. 4, showing a feature of the control for the brake, Fig. 4;

Fig. 12 is a detail view in section for control of a pneumatic device shown at the inactive position;

Fig. 13 is a view of the device of Fig. 12 at an intermediate control position;

Fig. 14 is a view of thedevice of Idg. 12 at the fully thrown position for control;

Fig. 15 is a fragmentary view of the operator station as to controller manipulations for installation with the transmission hereunder;

Fig. 16 is a hydraulic brake adaptable to the assembly in lieu of the showing in Fig. 3;

Fig. 17 is a detail view of features of the control cam for the accelerator pedal mechanism of Fig. 15;

Fig. 18 is a detail view of a more readily -adjustable relief for control of the brake of the general type of Fig. 16; I

Fig. 19 is a detail view of the pneumatic device adapted to be controlled by the accelerator pedal in Fig. 15, at the idle position therefor;

(01. 'u-zssl Fig. 20 is a view ofv the device of Fig. 19 for brake control at an intermediate position; f

Fig. 21 is a view similar to Fig.' l9 of the pneumatic brake control at fully thrown orlactive 'position; and I L 5 Fig. 22 is a view of hydraulic adaptations for control in applying frictional resistance in lieu of fluidpump.

From a prime mover as an internal combustion motor, there maybe actuation of shaft '1 inhous- 10 ing section 2 (Figs. 1, 2). This shaft J is mounted in bearings 3 and extends therepast to carry flange 4 having overhang 5' for annular'gear 5. concentrically with this shaft i, there is flange 1 having bearings 8 for stub shaft '9. This stub 15 shaft 9 protrudes, through the bearings 8, and carries pinion I0 fixed therewith and in mesh with annular gear 5 at the overhang 5'. Bolts H through the flange I assemble housing section l2 and inwardly extending flange 13- with the flange 2 I. There is thus provided in this planetary gearing system of this planet'pinion Ill and the annular gears 5, pump pinion keyedon the stub shaft 9; g

This pump pinion i4 is in annular series with pinions IS in this housing 1,12, i3. Filling plug l5 (Fig. 5) may be removed through opening H as screws ll permit removal, of plate I! on casing section 20. The hydraulic medium, as oil. may thus be introduced and churned into the casing l, I 2, I3, for filling such'structure with the pumping action taking place from intake ducts2i past the meshing gears in pairs to exhaust ducts 22.

Fixed on the stub shaft 9 and outside the planetary housing and hydraulic device for control of the same is gear 25. This stub shaft 9 is eccentric of the shaft I in its extent from the planetary gearing housing. This gear 23 thereby receives rotation from the shaft I through the annular gear 5, pinion Iii, stub shaft'S, gear 23 to pinion 24, connectable to shaft 25. This shaft 25 has bearing 26 in the flange l3 of the pump housing or hydraulic control of the planetary gearing sys- I tem. This shaft 25 has fixed therewith pinion 21 adjacent bearing 28 for this shaft 25. This bearing 28 is in arm 29 asv a crank or eccentric from shaft 30 in alignment with the shaft l and mounted in bearings 3|.

On this shaft 30, adjacent the bearings 3i, are bearings 32 for flange 33 carrying annular gear 34 in mesh with the pinion 21. This annular gear 3 has external tooth region '35 which may be held or controlled by pinion 36. This is for the intermediate speed transmission.

For first or low speed transmission, there is 8. The gear 81, as well as the diiferent diameter gear 28, are eccentric to the axis of the planetary gearing. This bearing 88 is in arm or crank 88 of the shaft 88 and is shown at 180 from the crank or arm 28. The pinion 81 is in mesh with gear 48, freely rotatable on sleeve 4| on the shaft 28. Connectable with this gear 48 is pinion 42 adjacent the pinion 21 and rotatable relatively thereto. This pinion 42 is in mesh with annular gear 48 spaced by bearings 44 from the gear 84 and by bearings 48 from holding plate 48 in the casing 88. This annular gear 48 has external toothed portion 41 and is in this respect similar to the annular gear 84 having the external tooth portion 88. The holding or control of this annular gear 48 is effected by pinion 48 adjacent the pinion 88. This gear 48 (Fig. 6) is in minor casing 48 having screws 88 removable to take of! plate II so that hydraulic medium may be poured into receptacle 82 in the upper portion of this casing 48, to flow by port 88 into a region about the pumping gear 48 and its companion pumping gear 84, with flow from port 88 by duct 88 and thence by riser 88. It is thus seen that with the gear 41 held for the first or low speed transmission, the rotation of the pinion 42 is effective through the shaft 28 to cause the crank 28 to rotate the driven shaft 88. When the connection for the hydraulic control gear 88 holds the gear 84, a higher speed of rotation is effective for this shaft'28 which disconnects the gear 48 from the pinion 42, due to the action of overrunning clutch 81. v

This withdrawal action is eflective in the overrunning against the normal transmission action of the helical teeth of the gearing. The operation may be such that there is overrunning, say from the shaft 88 or the crank 28, even as to the pinion 24, thereby effecting release of overrunning clutch connection 88 with the sleeve 4I which connects this pinion 24 with the pinion 21.

In the housing there is partition wall 58 carryi g the bea. ng 8| (Figs. 2, 4). Spline connection 88 on the shaft 88 holds collar 8I and overhang 82 for rotation with this driven shaft 88. This overhang 82 has an annular tooth portion 88 effective as the collar 8| is moved toward the bearing 8| to bring this annular tooth portion 88 as a jaw device into mesh relation with tooth portion 84, fast with shaft 88, in alignment with the shaft 88 and having a cooperating bearing. 88 therebetween. Tl'iis shaft 85, has bearing 81, and protrudes through housing wall 88 of casing 88. This is in the direct or forward drive transmission or connection for the device. If the collar 8| be shifted to an intermediate position at clearance region I8 as to the tooth member 84, there is a neutral or nondriving relation. At the remote position from the bearing 8| the portion 88 is in mesh with tooth portion II fixed with sleeve 12 which has laterally thereof a toothed portion in mesh with gear 18. (Fig. 10), fixed with shaft I4. Also fast on this shaft 14 is gear 15 (Fig. 3). This pinion I is in mesh with gear I8 in housing 11. The gear 18 is in mesh with pinion I8 fixed with the shaft 65. This housing 11 in casing 88 is normally sufficiently submerged to have a liquid 18 therein for hydraulic control of this hydraulic device with intake port 88 and exhaust port 8|.

Adjacent the wall 88 is spider 82 (Fig. 4) fixed on the shaft 85. Compression helical spring 83 normally thrusts collar 84 away from this spider fixed on the stub shaft 8 adjacent the gear 28. 'pinion 81 adjacent the bearing 88 for this shaft 82. This collar 84 has pins 88 coacting with arms 88 having pivotal mountings 81 on the spider 82. These arms 88 are inwardly extending and form portions of levers which have beyond the fulcra 81 arms 88 to fiy weights 88. There is accordingly herein provided a centrifugal speed device effective through the collar 84 to operate arm 88. This arm 88 is connected by link M to plunger 82 (Fig. 2), extending through the partition 88 and having balanced valve port 88 effective as a valve device for controlling fiow into the receptacle 82 (Fig. 6) by exhaust port 84 past this valve 88 to effect by hydraulic control the pumping action of the gear 88. At the open position the gear 88 is freely rotatable and there is no holding action for .the annular gear 84. This plunger '82 extends past this housing for the selective gear through the partition or diaphragm 85 which carries the bearing 8. This plunger 82 in the housing 2 has depending arm 88 coacting with collar 81 on the shaft I. This collar 81 is connected to sleeve 88 extending into the housing I8 and is there provided with port 88 controlling the intake 2i to this planetary hydraulic control. The circulaton to this intake port 2| is from the duct 22 through tubular terminus I88 of this sleeve 88 to the port 88. That position of this plunger 82 which efl'ects shifting of this sleeve 88 into cut-off position for the exhaust duct 22, looks this hydraulic control of the planetary gearing so that the pinion I8 does not rotate relatively to the annular gear 8, and there is a revolution of the shaft 8 instead of rotation. This revolution of the shaft with the crank 88 carries the crank 28 therewith and'eifects the direct rotation of the shaft 88 at the speed of the shaft l.

The arm 88 is connected through toggle MI with arm I82, located adjacent the arm 88 and extending to collar I 88 on the shaft l adjacent the collar 81. This collar I88 is'connected to plunger I84 in the sleeve 88 and is operable to close the port 88 independently of the position of the sleeve 88. Accordingly, in this position there is a locking of the planetary gearing. This is a position which cuts off reverse fiow and precludes free wheeling. It thus follows that when the port 88 is left open by the plunger I84, free wheeling may occur. In the previous looking for the direct drive, the shaft I was taken as having a controlling speed beyond that of the car. In the event the car, while connected for high speed or direct driving, has a speed beyond that of the motor, such may not be effective to reverse any flow condition in the planetary gearing hydraulic control when this device I84 closes the ports 88, for then the overrunning is taken into account at the clutches 58 and 51. It is thusseen that, as to the first and second speeds, there is free wheeling due to the overrunning action permitted in these clutches and that selectively such may be effective in high speed by breaking the toggle I8I.

Fixed with the shaft I is spider I85 as a mounting for fly weight I88 connected to collar I8'I. This collar I81 is connected by arm I88 to plunger I88, parallel to the plunger 82. This plunger I88 has balanced port valve device II8 effective adjacent the valve device 88 in controlling the exhaust port 58' and thus acting upon the gear 48 in the holding of the gear 41 for first speed driving. The arm 88 is connected to plunger I I I (Fig. 4) extending to housing II2 adjacent casing enlargement II3. In this housing II2 (Figs. 12, 13, 14) is diaphragm H4 fixed with the plunger II I.

Compression helical spring II normally tends to thrust this diaphragm of the diaphragm device toward the arm 90.

This spring II 5 is about a stem extension from 5 the plunger III having port II8.

extends to valve I20 (Fig. 12). Manually controllable plunger I2I is shiftable in this chamber I23. At inoperative position for the diaphragm II4, minute seepage port I22 from housing I2 is in communication by valve I24 of the plun r I2I with outlet port I25. Port I25 from the chamber I23 has seepage branch I21 controlled by valve I28 to seepage port I29. Shifting of the plunger I2I to intermediate position (Fig. 13) may be effected by connection I 2| (Fig. 15). The port H5 in the extension of the plunger III is still open to the passage in the housing I23 so that go seepage may occur by the port I22. This may be .a poise condition with the port I23 effective from the duct II1 for there is closed oi! the seepage I29. The end of the extension oi? v the plunger I I I acts as-its own cut-ofl valve which it moves past 25 the end of the passage in the. housing I23. The port I I5 in the extension of the plunger I II is still open to the passage in the housing I23 so that seepage may occur by the port I22. Further shifting of this plunger I2I by the manual control connects the suction .duct II1 to the valve I28 with duct I30 to the diaphragm chamber, thus effecting full throw for the plunger II I against the action of the spring I I5. There is no seepage now because the valve I24 has closed the seepage port I25.

Here is a supplemental influence .manually brought into play in addition to the speed influences for controlling this transmission. with the internal combustion engine eflective for creating a vacuum, the arm 90 may transmit the influence thereof through the link 9I to the plunger 92. However, this influence is only as modified by the fly weight device 89 actuated by the driven shaft 55, which may extend to the propeller shaft of the automobile.

This is an influence upon the speed relations between intermediate and high as effective through the gear 34 and for the hydraulic device at the gear 35, and through the arm 33 as effective at the planetary hydraulic device through the gear I4. It is to be noted that the transmission is not effective until the motor speeds up and the fly weight device I05 is effective through the hydrauliccontrol at the pump gear 48 in effecting holding for the gear 43.

This unit accordingly involves in the series, an automobile clutch for connecting into flrst speed or starting of the motor with automatic shifting therefrom as the drive shaft picksup speed. This may be influenced by the labor of the motor for modifying the travel rate of the vehicle at which the change speeds become eflfective through the pneumatic device. There is thus a provision in the hydro-pneumatic control that there may be automatic speed connection as the motor is in certain driving relations and the vehicle is in certain speed relations. This means that the con- Suction duct II1 (Fig. 12) is connected to intake manifold II3 of internal combustion motor II 9 (Fig. 15) and in speed at high through flexible wire I3I (Fig. 2)

to break the toggle IOI. This flexible wire may be influenced by dash control (Fig. 1). The direction of travel is eflectedthrough the shifting of the collar 8| by fork I32 (Fig. 4) having resistance ball I33 coacting with seats I34- on stem I35 projecting from the partition; This shifting of the arm I32 is efleoted by flexible wire I38 for reverse forward and neutral positions of the seats I34. This shifting is manually eifected and this wire I35 extends to a position for the operator to control at pull I31 on dash I38 (Fig. 1). Adjacent this direction control handle I31 (Fig. 1) may be located free wheeling control handle I39.

In carrying out this invention, instead of having the wire I3I for the free wheeling directly connected to the pull handle on the dash, such wire I3I may extend to pin I40 (Fig. 17) in way I of cam plate I42 connected to be shifted by flexible-transmission connection I43 extending to pull button I44 on the dash I33 (Fig. 15). The operator station herein is shown as equipped with accelerator pedal I45 having fulcrum mounting I48 at foot board I41. This accelerator pedal I45 has link I48 therefrom to lever I49 having flxed fulcrum I50. Spring I5I acts normally to hold the foot pedal or accelerator pedal lifted. Fixed with this lever I49 is arm I52 having link I53 extending to carburetor I54. This position of the arm for the carburetor control may be adjusted by stem I55 as to abutment I55 carried by the lever I49. The position of this lever I 49 relative to the foot board I41 is adjusted by this flexible transmission connection I43 by acting on the plate I42, for this plate I42 (Fig. 17) has cam side I51 acting upon this lever I49 determining the position given this pedal I45 by the spring I5I. The cam way I determines that free wheelin may be cut out, but when free wheeling is cut out the cam I51 is effective for locating a no-brake position I58, a. position I59 for fluid brake full setting, and a position I for friction brake setting in addition to the fluid brake setting.

The fluid brake setting through the accelerator pedal is effected by flexible transmission connection I5I connected to operate member I52 (Fig. 11). It is thus seen there is a lever device for brake control by foot pedal instead of a separate emergency brake lever or even a separate foot brake pedal. coincidentally with this control action of the lever I49 as to the flexible transmission connection I5I, there, is operator I53 (Fig. 15) extending to housing I54 (Fig. -19), from which extends link I 55 to operate friction brake arm I55 (Fig. 2) adjacent the rear axle of the vehicle. This housing I54 has therein sleeve I51 with port I88 exposed to fluid power line I59. At idle position for the accelerator pedal, diaphragm I10 is toward the link.l55. In pulling the sleeve I51, port I1I is pulled out of register with port I12 thus cutting off escape to the air, and port I13 approaches register with port or clearance I14, with the diaphragm'l10 at intermediateposition. Further action of the flexible transmission connection I 53 brings the port I13 again to register with the port I14 and the shifting of the diaphragm I10 closes ofl' port I13 and holds the brake in this fully thrown or active position. This sleeve I51 in the housing I54 has recover and slack take up for the flexible transmission connection I 53 in helical spring I15 extending to pin I15, connecting the link-I55 with sleeve I11.

. against excessive pressure in such braking device. Instead of this relief being pre-set (Fig.

16), there may be manual adjustment of the braking action relief by supplemental manual control I84.

. This flexible transmission connection I84 (Fig.

18) may extend to the dash I38 to be operated by handle I90 Fig. 15) to arm I85 (Fig. 18) effective through cam I86 acting on plunger I81,

to vary the compression action of spring I88 on :20 poppet valve I89. In the matter of getting the car under way the first thing is to turn on ignition switch I9I. There is thus in this instance a manual control for the holding or braking operation as hydraulically effected on the driven -25 shaft.

In operation the one in the car may turn on the ignition switch I9I (Fig. 15), say as interconnected to the starter, and the motor will begin to function. The connections and controls may -30 be so set that the driving shaft I is running idly until there is a speed of say 500 R. P. M. In the power controls herein shown, instead of being interconnected with the electrical system or fully fluid, they are shown as involving speed -35 functions as to the driving source and the driven weight device I06 may be efiective to so shift the valve plunger I09 that there is congestion of the exhaust from the hydraulic control in first speed of the gear 43. Driving is thus effected :45 at this speed, which driving is automatic and as the motor shaft I builds up to, say a speed of 600 or more R. P. M., then the driven shaft 65 may have a speed of say 250 R. P. M. At this speed the valve plunger 92 may have the hydraulic con- 50 trol for the gear 34 open to the exhaust. As this speed increases, say above 250 R. P. M. for the driven shaft 65, automatic power control or fly weight device 89 may operate to shift the plunger 92 into closed position for the valve 93 for the 55 car to be operating in second speed.

This is regardless of whether the plunger I09 has the valve IIO open or closed. As this has choked down the speed of the motor, the device I06 may open the valve IIO, while if the speed go is still retained, there may be overrunning or free wheeling of this second speed relatively to the first speed, due to the overrunning clutch device 51. As the speed of the driven shaft 65 builds up to, say 500 R. P. M., the-plunger 92 may be so 65 shifted not only to retain the valve 93 closed but also to operate the valve sleeve 98 to choke or cut-oif exhaust 22. This may be at the speed of say ten miles per hour for the car, which is thus thrown into high or direct drive through 7 the hydraulic device of the planetary system being locked. As the speed of the driven shaft 65 increases, the fly weight device 89 has greater influence. However, this influence may be modified due to the diaphragm device Hi. This de- 7 vice may be considered as'a torque modifier.

Initially, the setting may be one, say that for the automatic shifting from first speed to second to occur at say seven miles per hour, and from second to third or high at sixteen miles per hour. It is to be noted in these drives or con- 5- nections hereunder that the gears are in mesh with each other at all times and there is thus advantage in the free wheeling as herein disclosed. In the automatic-devices hereunder, it

is further to be noted that'the control to start the car depends upon the speed of the engine. The control to shift from first speed into second or third depends upon the speed of the car, which is thus of course modified by the load on the engine, and this load on the engine or speed 5 at which these changes are to occur may be influenced manually by the operator of the car, as herein disclosed. in the position for the accelerator pedal. Depression of the pedal may shift the control so that the change from first to second occurs at ten miles and from second to high, at thirty-five miles. Accordingly, there is an influence on this automatic control as brought about by the position of the accelerator pedal.

A convenience under the installation of the transmission herein involving starting, say by rolling the car, may be effected by shifting the control into high with free wheeling cut-out. Thus as the car is pushed, the motor may in its starting automatically pick up in this high speed, and as the transmission is effective, step itself back into second and first. There is economy in the braking hereunder on the shaft 65, herein shown as hydraulic, over that say of allowing 35 the motor to brake the car, for in the operation under the device of this disclosure. there is not required a consumption of gasoline by the motor nor oil at the motor forthis hydraulic braking may be directly on the system itself. 440

In order that there may not be resistance to the shifting into freewheeling or in the manipulation as to the planetary hydraulic device, the plunger I04 may not be unduly resisted by trapped liquid, due to bypass relief device I92 (Fig. 2). In the matter of the overrunning clutch, angular pick up may be facilitated through springs I93 (Figs. 8, 9) to act between cam jaw faces I94, I95, in expanding such for frictional gripping with collars I96, I91. This holding action is effective for minimizing delay in transmission pick up.

The driven shaft 30 has therefrom fork I98 (Fig. '7) connected by the bolts II with the planetary housing I3. Accordingly there is the direct high speed drive when this housing I3 rotates with the driving shaft I. This fork I98 is the direct connection with the shaft 30 past the first and intermediate speed gears.

The number oftoothed gears may be materially reduced with retention of flexibility of control, except that it is in a general set up involving, as herein shown (Fig. 22) elimination of the feature of free wheeling. To this end, hydraulic pressure is supplied for say the first speed control from the drive shaft I through pump I99 connected by duct 200 to housing 20I, valve 202 as an adjustable check. As pressure is built up in this chamber 20I and fly weight device I06 has a position to throw in the speed, there is transmission by the way of the arm I08 and plunger I09 to locate port 203 for flow of the pressure fluid from the duct 209 by way of the valve 202 and passage 203' for communication through the diaphragm 96 with hydraulic chamber 204. It is desirable to have the pressure at the relief valve, say a ten pounds pressure, so that operation does not occur here until the pressure is built up, although this fluid may be a lubricant as a part of the circulating system. This chamber 204, together with intermediate friction plate 205 is held to non-rotary plate diaphragm 46 by bolt 206. This chamber 204 includes plate 201 normally thrust clear or away from intermediate plate 208 by compression helical spring 209. Between the plate 208 and plate N0 of the chamber 204 are a plurality of slidable friction disks 2 spaced by stationary similar plate 205. These plates 2| l have key assembly at key portions 2! with the gear 43. Accordingly, as pressure is developed in the chamber 204, there is frictional gripping through these plates 205, 2, 208, 2l0, for applying frictional resistance in holding the gear 43. There is thus a connectingin of the device for first speed driving. The release of pressure at the chamber 204 as well as in the casing 2M and the overflow is by duct 2l3 back to the pump I99.

For the control after the driven shaft 65 has come into operation, fluid pressure may be supplied by pump 2l4 on the shaft 65 or there may be a connection from the hydraulic brake (Figs. 10, 18). Fluid flow under pressure from this pump 2l4 may be by duct 2|5. Relief valve 2l6 in housing 2!! may have passage 2l8 for fluid return to the pump 2l4. This duct 2l5 may have flow therefrom controlled by plunger 2l9 cooperating in a somewhat analogous manner to that of the plunger 92. This plunger 2I9 as associated with the lever 90 in the building up of speed of the driven shaft 65 may respond to the operation of fly weight 89 and bring port 220 to permit flow of pressure liquid by line Hi to hydraulic chamber 222, oppositely disposed as to the spacer plate208 from the chamber 204. This chamber 222 has plate 223 anchored by the pin 206 and also plate 224, which laterally shiftable plate is engaged by the spacer spring means 209.

Rotatively fixed with the gear 34 but free for lateral shifting thereon is a plurality of friction plates 225 spaced by friction plate 226 anchored with the pin 206. Expansion of the chamber 222 under hydraulic pressure causes the plates 224, 226 and 208 to grip the plates 225 and hold such against rotationand thereby lock the gear 34. This effects the second speed driving as distinguished from the first speed driving and allows the overrunning to automatically cut out the transmission as would otherwise be effective through the gear 43.

Further building up of pressure or speed has its response at the lever 90 for check valve 221- to open from the duct 2l5 and allow flow as controlled by the port 220 by duct 228 to hub 229, thereby to connect duct 230 in the shaft 30. This duct 230 extends through the extension from this shaft 30 to plate 2: in substitution for the plate [3 at the planetary gearing housing.

This plate 23l has bolts 232 mounting plates 233, 234, as spaced by spring means 235. Additionallf there is a shiftable friction disk 236 held by these bolts 232. The overhang 5 from the internal gear 6 has external keying means 231 holding as free for lateral shifting but againstangular movement a plurality of friction disks 238 to be-gripped by the disk and plates 236, 233, 234, as fluid pressure from the duct 230 is communicated by branch 239 to charge chamber- 240, thereby locking the planetary gear l0 with the gear 6 for direct rotation so that the driven shaft 30 is at the same rotative speed as the shaft l.

The setting of the valve 202 may be at, say about ten pounds pressure. The valve 22'! may operate, say at thirty pounds pressure in the cutover from second speed to high or direct drive. The relief valve 2I6 may be set at, say around forty pounds. When the vehicle slows up so the governors or speed devices 89 and I06 are inactive, then there is of course release of pressure in these systems, while additionally there is not the operation f the pumps to build up such pressures. The 1 ilftings from second into third speed are influenced by the diaphragm device connected to the lever I l I which is a prime mover influenced control.

What is claimed and it is desired Letters Patent is:

to secure by A transmission embodying a driving shaft, a-

driven shaft, axially offset intermediate shafts, a governor for the driving shaft, an additional governor for the driven shaft, gearing between the driving and driven shafts including planetary gears on the intermediate shafts, hydraulic braking mechanism actuable from the driving shaft governor, a second hydraulic braking mechanism actuable from the driven shaft governor, and a control affecting connection between the driving and driven shafts as to the mechanisms and gearing, said control including a vacuum responsive valve for influencing a hydraulic braking mechanism.

ESTEL O. WHEATON. 

